US20200032888A1 - Final drive for a motor vehicle - Google Patents
Final drive for a motor vehicle Download PDFInfo
- Publication number
- US20200032888A1 US20200032888A1 US16/337,592 US201716337592A US2020032888A1 US 20200032888 A1 US20200032888 A1 US 20200032888A1 US 201716337592 A US201716337592 A US 201716337592A US 2020032888 A1 US2020032888 A1 US 2020032888A1
- Authority
- US
- United States
- Prior art keywords
- bearing
- ring gear
- final drive
- output shaft
- boss
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/12—Differential gearings without gears having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/121—Power-transmission from drive shaft to hub
- B60B35/122—Power-transmission from drive shaft to hub using gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/14—Torque-transmitting axles composite or split, e.g. half- axles; Couplings between axle parts or sections
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
- B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/037—Gearboxes for accommodating differential gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
- F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
- F16H2057/02052—Axle units; Transfer casings for four wheel drive
Definitions
- the invention relates to a final drive for a motor vehicle for a motor vehicle, comprising a first input shaft, a second input shaft, a first output shaft, and a second output shaft, wherein the first input shaft is permanently coupled to the first output shaft by means of a first ring gear transmission and the second input shaft is permanently coupled to the second output shaft by means of a second ring gear.
- the final drive is coordinated with an axle of the motor vehicle, such as a front axle, but preferably a rear axle of the motor vehicle.
- a torque is transmitted from a drive mechanism of the motor vehicle to wheels of the motor vehicle.
- the final drive produces or at least can produce an operative connection between the drive mechanism of the motor vehicle and the axle or its wheels.
- the drive mechanism is coupled or at least can be coupled permanently to the first input shaft and the second input shaft.
- the operative connection between the drive mechanism and the two input shafts is present through a transmission mechanism different from the final drive.
- the transmission mechanism may be designed, for example, as a differential transmission, especially an axle differential transmission.
- the two input shafts may accordingly be present as Cardan shafts or at least be coupled to Cardan shafts, especially in permanent manner
- the two input shafts of the final drive are permanently coupled to the output shafts of the transmission mechanism, especially in rigid manner
- the two output shafts of the final drive are provided at the wheel side, i.e., arranged on a side of the ring gear transmission facing away from the drive mechanism in relation to the flow of torque.
- the first output shaft for example is associated with a first wheel of the axle and the second output shaft is associated with at least with a second wheel of the same axle, especially coupled to it in a permanent and/or rigid manner
- a shift clutch is provided in the operative connections, especially a claw clutch.
- the first input shaft is permanently coupled to the first output shaft and the second input shaft is permanently coupled to the second output shaft.
- the first ring gear transmission and the second ring gear transmission serve for this purpose.
- an angled arrangement of the input shafts and the output shafts to each other is achieved.
- the ring gear transmissions respectively have a hypoid offset, so that the output shafts are arranged with an offset relative to the input shafts, in particular they lie skew to them, i.e., they are arranged at a parallel spacing from them.
- the problem which the invention proposes to solve is to propose a final drive for a motor vehicle which has advantages over known final drives, especially a reliable mounting of the ring gear transmissions at the same time as having less design space requirement.
- first input shaft and the second input shaft are arranged coaxial to each other and the first output shaft and the second output shaft extend from the respective ring gear transmission in opposite directions, wherein an axis plane contains the axes of rotation of the input shafts and a plane perpendicular to the axis plane makes an angle of at least 75° and at most 90° with each of the axes of rotation of the output shafts, and that a first ring gear of the first ring gear transmission, which first ring gear is rigidly connected to the first output shaft, and/or a second ring gear of the second ring gear transmission, which second ring gear is rigidly connected to the second output shaft, is mounted in a transmission housing of the final drive in each case by means of a first radial bearing and a second radial bearing, which are arranged in tandem arrangement or in X arrangement to each other or are designed as a fixed bearing and as a floating bearing.
- the two input shafts are arranged coaxial to each other.
- the second input shaft extends in the first input shaft or vice versa.
- the two output shafts lie substantially opposite one another, especially in regard to the plane of symmetry, and they extend from the respective ring gear transmission in opposite directions, preferably in the direction of the corresponding wheel of the motor vehicle.
- Both the axis of rotation of the first output shaft and the axis of rotation of the second output shaft for example intersect the two axes of rotation of the input shafts or the common axis of rotation of the input shafts.
- axes of rotation of the output shafts each intersect the axes of rotation of the input shafts.
- the ring gear transmissions may be designed without a hypoid offset.
- a design with hypoid offset may also be realized, in which therefore at least the axis of rotation of one of the output shafts does not intersect the axes of rotation of the input shafts.
- the axes of rotation of both output shafts do not intersect the axes of rotation of the input shafts in this case.
- the (imaginary) axis plane contains the axes of rotation of the input shafts.
- the axis plane is arranged substantially horizontal in regard to the installed condition of the final drive. Accordingly, the plane perpendicular to the axis plane, and likewise containing the axes of rotation of the input shafts, is present as a vertical plane, i.e., it is arranged substantially vertically in the installed condition of the final drive.
- the plane perpendicular to the axis plane at least seem in sectional view, namely, especially in the cross section relative to the axes of rotation of the input shafts, makes an angle of at least 75° and at most 90° with the axes of rotation of the output shafts.
- Each of the axes of rotation thus makes an angle with the plane that fulfills the mentioned preconditions.
- the angles between the axes of rotation and the plane may be identical, or alternatively they may be different from each other.
- the angles amount to at least 75° and at most 90°.
- the angle or the angles amount to at least 80°, at least 85°, at least 86°, at least 87°, at least 88° or at least 89°, but always at most 90°. This means that the angle or the angles may be precisely equal to 90° or also less than 90°.
- the plane perpendicular to the axis plane is the plane of symmetry for the axes of rotation of the output shafts at least when seen in sectional view, namely, in particular in the cross section relative to the axes of rotation of the input shafts.
- the axes of rotation of the output shafts in this case are thus oriented or arranged symmetrically to one another in regard to the plane of symmetry.
- the first ring gear is rigidly connected to the first output shaft and the second ring gear to the second output shaft.
- the first ring gear is part of the first ring gear transmission
- the second ring gear is part of the second ring gear transmission.
- At least one of these ring gears, but preferably both ring gears, are now mounted in the transmission housing of the final drive, each time by means of two radial bearings, namely, the first radial bearing and the second radial bearing.
- the two radial bearings are situated in a tandem arrangement or in an X arrangement relative to each other. Alternatively, they may also be designed as a fixed bearing and as a floating bearing.
- one of the radial bearings forms the fixed bearing and the other of the radial bearings forms the floating bearing.
- Such an arrangement and/or configuration of the radial bearings enables a reliable and compact mounting of the ring gear or the ring gears on and/or in the transmission housing.
- a further embodiment of the invention provides that the axes of rotation of the two input shafts and the axes of rotation of the two output shafts lie in the axis plane. This represents an especially advantageous orientation of the input shafts and the output shafts, allowing an extremely compact configuration of the final drive. If both the input shafts and the output shafts are arranged in the axis plane, the definition given above using the plane of symmetry is not needed. Accordingly, this is no longer necessary for the definition of the axis plane.
- a further especially preferred embodiment of the invention provides that a bearing element is arranged in the transmission housing, comprising a first bearing boss and a second bearing boss, wherein the ring gear of the first ring gear transmission is mounted on the first bearing boss and the ring gear of the second ring gear transmission is mounted on the second bearing boss.
- the bearing element is arranged in the transmission housing.
- the bearing element comprises the two bearing bosses, namely, the first bearing boss and the second bearing boss.
- the bearing bosses serve for the mounting of ring gears of the two ring gear transmissions. Accordingly, the first ring gear of the first ring gear transmission is mounted on the first bearing boss and the second ring gear of the second ring gear transmission is mounted on the second bearing boss.
- the mounting is preferably directly configured so that the respective ring gear sits on the corresponding bearing boss.
- a merely indirect mounting may be provided, in which for example the ring gears are mounted on the bearing boss via the respective output shaft.
- the output shaft is mounted directly at or on the bearing boss.
- the mounting of the respective ring gear is provided only indirectly across the output shaft.
- the ring gear may be spaced apart from the bearing boss in the axial direction with respect to its axis of rotation or the axis of rotation of the output shaft.
- the first ring gear is rigidly joined to the first output shaft or alternatively forms a single piece with it.
- the same may be provided for the second ring gear and the second output shaft.
- the bearing element is a mechanism designed separately from the transmission housing.
- the bearing element is arranged centrally in the transmission housing, especially centrally with respect to the axes of rotation of the two input shafts.
- the axes of rotation of the two input shafts extend through the bearing element, i.e., they intersect it.
- the latter is preferably multi-piece and comprises for example a first housing shell and a second housing shell.
- the two bearing bosses for example are round in cross section with respect to their respective longitudinal center axis and preferably emerge in the axial direction from a center post of the bearing element. At their end facing away from the center post, the bearing bosses preferably have a free end.
- a preferred embodiment of the invention provides that the first radial bearing is arranged on the first bearing boss or the second bearing boss for the mounting of the respective ring gear, and/or the second radial bearing is arranged on the transmission housing.
- the first radial bearing is arranged on the first bearing boss or the second bearing boss for the mounting of the respective ring gear, and/or the second radial bearing is arranged on the transmission housing.
- only one of the two radial bearings i.e., the first radial bearing and the second radial bearing, is arranged on the first bearing boss, if it is serving for the mounting of the first ring gear, and on the second bearing boss, if it is provided for the mounting of the second ring gear.
- the radial bearing on the bearing boss By the arrangement of the radial bearing on the bearing boss is meant that it sits by its inner ring on the respective bearing boss. This means that its inner ring entirely encloses the bearing boss in the circumferential direction and lies against it preferably at least partly continuously, especially entirely continuously, in the circumferential direction. Conversely, this means that the outer ring of the radial bearing engages with the respective ring gear.
- a mounting of the ring gear on the transmission housing is provided at least partly via the corresponding bearing boss, so that the ring gear is mounted indirectly on the transmission housing, namely, across the respective bearing boss.
- the second radial bearing engages on the one hand with the transmission housing and on the other hand with the ring gear or the corresponding output shaft.
- the second radial bearing sits by its inner ring on the ring gear or the output shaft.
- the outer ring of the second radial bearing may be fastened to the transmission housing.
- one of the radial bearings is arranged on one of the bearing bosses and the other radial bearing engages with the transmission housing.
- the ring gear mounted with the aid of the two radial bearings namely, the first radial bearing and the second radial bearing, is mounted between the bearing boss and the transmission housing, namely, indirectly mounted.
- the ring gear is mounted across the first radial bearing directly on the first bearing boss and accordingly indirectly on the transmission housing.
- the ring gear is mounted across the second radial bearing directly on the transmission housing. This allows for an especially advantageous bracing of the ring gear or the ring gears in the axial direction with respect to their particular axis of rotation.
- a further embodiment of the invention provides that the first radial bearing lies against an inner bearing face of the respective ring gear and the second radial bearing lies against an outer bearing face of the respective ring gear or the output shaft connected to the ring gear.
- the inner bearing face is formed by a region of the inner circumferential face of the ring gear.
- the ring gear accordingly has a recess formed coaxial to its axis of rotation or the axis of rotation of the corresponding output shaft.
- the radial bearing now engages with this recess.
- the respective bearing boss protrudes into the corresponding ring gear in the axial direction.
- the bearing boss reaches through an end face of the ring gear, especially an end face of the ring gear facing toward the bearing element.
- the second radial bearing engages with the outer bearing face or lies against it.
- the outer bearing face is formed by an outer circumferential face of the ring gear or the output shaft, which is connected to the ring gear.
- the first radial bearing lies against the ring gear or the output shaft, spaced apart in the axial direction from the second radial bearing.
- the two radial bearings should accordingly engage with the ring gear or the output shaft at places spaced apart in the axial direction, especially in order to prevent a tilting of the ring gear or the output shaft.
- the first bearing boss and the second bearing boss emerge from a center post of the bearing element.
- the center post is accordingly present between the two bearing bosses, which emerge from it on opposite ends of the center post.
- the center post is arranged roughly centrally in the transmission housing, preferably centrally with respect to the axes of rotation of the input shafts.
- the axes of rotation of the input shafts extend at least through the bearing element, but especially through the center post.
- an especially preferred embodiment of the invention provides that the second radial bearing is braced against the transmission housing in the axial direction with respect to the axis of rotation of the respective ring gear.
- the second radial bearing rests for example by its outer ring against the transmission housing, while it encloses the ring gear or the output shaft with its inner ring.
- the transmission housing has an axial bearing boss, in order to secure the second radial bearing in the axial direction relative to the transmission housing, on the outside at least in the axial direction, that is, in the direction facing away from the bearing element.
- the ring gear likewise comprises an axial bearing boss, so that the second radial bearing as a whole, looking in the axial direction, lies on the one hand against the axial bearing boss of the ring gear and on the other hand against the axial bearing boss of the transmission housing and the ring gear as a whole is secured or at least almost secured by the two radial bearings in the axial direction.
- the bearing element is fastened to the transmission housing, while the first radial bearing is connected to the transmission housing only via the bearing element.
- the bearing element is arranged in the transmission housing and secured to it.
- the bearing element lies against the transmission housing at least for a portion. This holds especially for the center post.
- the bearing element is secured by means of at least one screw to the transmission housing.
- the transmission housing is multi-piece in design and accordingly it has a first housing shell and a second housing shell. The two housing shells are formed separately from each other and preferably lie against one another in a plane of contact, situated in the axis plane or being parallel to it.
- the bearing element is fastened to the first housing shell and to the second housing shell, in particular, on opposite sides of the plane of contact or each time by means of at least one screw, whose longitudinal center axis is angled relative to the plane of contact and/or stands perpendicular to it. It may furthermore be provided that the bearing element is respectively fastened to the first housing shell and/or the second housing shell on both sides of an imaginary plane situated perpendicular to the plane of contact and containing a point of intersection of the axes of rotation of the output shafts with the axes of rotation of the input shafts.
- the radial bearing arranged on the first bearing boss or the second bearing boss is now connected to the transmission housing solely via the bearing element.
- the first radial bearing has a first inner diameter and a first outer diameter and the second radial bearing has a second inner diameter and a second outer diameter, while the first inner diameter is different from the second inner diameter and/or the first outer diameter is different from the second outer diameter.
- the difference between the first outer diameter and the first inner diameter is equal to the difference between the second outer diameter and the second inner diameter, so that the two radial bearings have identical dimensions, looking in the radial direction.
- first inner diameter is larger than the second inner diameter and/or the first outer diameter is larger than the second outer diameter.
- the first radial bearing is accordingly larger in configuration than the second radial bearing, but preferably the difference between the inner diameter and the outer diameter of the two radial bearings is identical in the manner explained above.
- FIG. 1 a schematic side view of a final drive for a motor vehicle
- FIG. 2 a schematic cross sectional representation through a transmission housing and a bearing element arranged in the transmission housing
- FIG. 3 a schematic representation of the final drive in a first embodiment
- FIG. 4 a schematic representation of a second embodiment of the final drive
- FIG. 5 a first variant of a third embodiment of the final drive in a schematic representation
- FIG. 6 a schematic representation of a second variant of the third embodiment of the final drive.
- FIG. 1 shows a schematic side view of a final drive 1 for a motor vehicle.
- This comprises a first input shaft 2 , of which a connection flange 3 is shown here.
- a second input shaft 4 Coaxial to the first input shaft 2 is arranged a second input shaft 4 not visible here.
- the first input shaft 2 for this purpose is designed as a hollow shaft and the second input shaft 4 is arranged and/or mounted in the first input shaft 2 .
- the second input shaft 4 has a connection flange 5 , which is preferably arranged in the connection flange 3 of the first input shaft 2 .
- the first input shaft 2 is permanently coupled by means of a first ring gear transmission 6 to a first output shaft 7 .
- the first output shaft 7 has a connection flange 8 , which can be seen here.
- the second input shaft 4 is permanently coupled by means of a second ring gear transmission 9 to a second output shaft 10 permanent, not visible here, having a connection flange 11 .
- the first ring gear transmission 6 consists of a ring gear 12 coupled rigidly and permanently to the first input shaft 2 and a ring gear 13 meshing with the ring gear 12 and coupled rigidly and permanently to the first output shaft 7 .
- the second ring gear transmission 9 comprises a ring gear 14 coupled rigidly and permanently to the second input shaft 4 and a ring gear 15 meshing with the ring gear 14 and coupled rigidly and permanently to the second output shaft 10 .
- the ring gear transmissions 6 and 9 and correspondingly the ring gears 12 , 13 , 14 and 15 are arranged in a transmission housing 16 of the final drive 1 , especially arranged entirely therein. In other words, the transmission housing 16 encloses the ring gear transmissions 6 and 9 preferably entirely.
- first input shaft 2 and the second input shaft 4 are arranged coaxial to each other, whereby the second input shaft 4 lies inside the first input shaft 2 .
- the input shafts 2 and 4 thus have mutually coinciding axes of rotation 17 and 18 .
- the first output shaft 7 and the second output shaft 10 now extend from the respective ring gear transmission 6 or 9 in opposite directions.
- the first output shaft 7 thus extends out from the plane of the drawing, while the second output shaft 10 extends into the plane of the drawing.
- One axis of rotation 19 of the first output shaft 7 or each connection flange 8 is arranged slightly slanting in the vertical direction and intersects the axes of rotation 17 and 18 .
- the input shafts 2 and 4 or their axes of rotation 17 and 18 lie in an axis plane 21 , which is situated basically horizontal.
- an imaginary plane stands perpendicular to the axis plane 21 , being the plane of symmetry for the axes of rotation 19 and 20 of the output shafts 7 and 10 , seen in sectional view, especially in the cross section with respect to the axes of rotation 17 and 18 .
- the axes of rotation 19 and 20 are accordingly oriented and arranged symmetrically to this imaginary plane, which on account of the horizontal arrangement of the axis plane 21 can also be called the vertical plane.
- the axes of rotation 19 and 20 intersect both the plane of symmetry and the axis plane each time by the same angle.
- the axis of rotation 19 thus makes a first angle with respect to the axis plane 21 or the plane of symmetry and the axis of rotation 20 makes a second angle with respect to the axis plane 21 or the plane of symmetry, the two angles being equal.
- the axes of rotation 19 and 20 intersect the axis plane 21 . It may also be provided that the axes of rotation 19 and 20 lie entirely in the axis plane 21 .
- the transmission housing 16 is multi-piece and comprises a first housing shell 22 and a second housing shell 23 , which are fabricated separately from each other and rest against one another in a plane of contact 24 , lying in the axis plane 21 or being parallel to it.
- the first housing shell 22 and the second housing shell 23 are joined together by means of at least one screw 25 , in the exemplary embodiment shown here by means of a plurality of screws 25 .
- At least one of the screws 25 but preferably all of the screws 25 , now has a longitudinal center axis 26 which is angled relative to the plane of contact 24 , i.e., which intersects it at a particular angle.
- the screw 25 or its longitudinal center axis 26 is arranged parallel to the plane of contact 24 or that the longitudinal center axis 26 lies in the plane of contact 24 .
- the longitudinal center axis 26 stands perpendicular to the plane of contact 24 .
- at least one of the screws 25 is penetrated by the plane of contact 24 , i.e., it is intersected by the plane of contact 24 .
- first bearing face 27 situated in the plane of contact 24
- second bearing face 28 situated in the plane of contact 24
- the two bearing faces 27 and 28 lie flush against each other, especially over the entire surface, after the assembling of the housing shells 22 and 23 .
- full-surface arrangement is meant that the entire first bearing face 27 lies against the entire second bearing face 28 .
- Each of the bearing faces 27 and 28 accordingly fully covers the respective other bearing face 28 or 27 .
- the screw 25 now passes through both the first bearing face 27 and the second bearing face 28 . Accordingly, it engages with the first housing shell 22 and with the second housing shell 23 to fasten them to each other.
- the first bearing face 27 extends in the direction of the axes of rotation 17 and 18 from one end 29 of the transmission housing 16 to its other end 30 .
- both the first bearing face 27 and the second bearing face 28 extend on the one hand as far as the end 29 and on the other hand as far as the end 30 .
- the bearing faces 27 and 28 may be interrupted. In the exemplary embodiment shown here, this is the case for both bearing faces on account of a first exit opening 31 for the first output shaft 7 or its connection flange 8 as well as a second exit opening 32 for the second output shaft 10 or its connection flange 11 .
- the first output shaft 7 accordingly passes through the first exit opening 31 or is situated therein, while the second output shaft 10 passes through the second exit opening 32 or is situated therein.
- the exit openings 31 and 32 are formed in equal parts in the housing shell 22 and the second housing shell 23 .
- at least each of the exit openings 31 and 32 lies at least partly in the first housing shell 22 and at least partly in the second housing shell 23 .
- the bearing faces 27 and 28 thus each comprise two partial faces, which are situated on opposite sides of the exit openings 31 and 32 , looking in the axial direction with respect to the axes of rotation 17 and 18 .
- FIG. 2 shows a schematic partial sectional representation of a portion of the final drive 1 .
- the input shafts 2 and 4 as well as the output shafts 7 and 10 are not shown here. This also applies to the ring gear transmissions 6 and 9 . Basically, however, reference is made to the preceding remarks. It is now clearly recognizable here that the axis of rotation 19 intersects the axes of rotation 17 and 18 at a point of intersection 33 . This also holds analogously for the axis of rotation 20 at a point of intersection 34 not shown here, which may coincide with the point of intersection 33 .
- a bearing element 35 is arranged in the transmission housing 16 in a preferred embodiment of the final drive 1 .
- This comprises a first bearing boss 36 and, situated opposite to this, a second bearing boss 37 , not recognizable here.
- Rotationally mounted on the first bearing boss 36 is the first ring gear 13 , rigidly connected to the first output shaft 7
- on the second bearing boss 37 is mounted the ring gear 15 of the second ring gear transmission 9 , rigidly connected to the second output shaft 10 .
- the first bearing boss 36 protrudes in the direction of the first exit opening 31 , in particular it protrudes into it or even passes through it in the direction of the axis of rotation 19 .
- the second bearing boss 37 protrudes in the direction of the second exit opening 32 . It also may protrude into it or even pass through it in the direction of the axis of rotation 20 .
- the bearing element 35 is now fastened on the one hand to the first housing shell 22 and on the other hand to the second housing shell 23 .
- the fastening occurs each time by means of at least one screw 38 , preferably each time by means of several screws 38 .
- This is recognizable here only for the fastening of the bearing element 35 to the second housing shell 23 .
- the corresponding remarks may be applied to the fastening of the bearing element 35 to the first housing shell 22 .
- the screw 38 or the screws 38 each have a longitudinal center axis 39 .
- the screw 38 or its longitudinal center axis 39 is now angled with respect to the plane of contact 24 (not shown here). In particular, it stands perpendicular to the plane of contact 24 . This means therefore that the longitudinal center axis 39 of the screw 38 is oriented preferably parallel to the longitudinal center axis 26 of the screw 25 .
- the screw 38 engages in a center post 40 of the bearing element 35 in order to hold the bearing element 35 on the transmission housing 16 .
- the bearing bosses 36 and 37 emerge from the center post 40 on opposite sides of the plane of symmetry.
- a through opening 41 may be formed in the center post 40 , especially between the bearing bosses 36 and 37 , to receive the second input shaft 4 .
- the second input shaft 4 passes entirely through the bearing element 35 , especially its through opening 41 , in the axial direction with respect to the axes of rotation 17 and 18 .
- the ring gear transmissions 6 and 9 are preferably configured such that the ring gears 12 and 14 connected to the input shafts 2 and 4 are present on opposite sides of the bearing element 35 , i.e., on opposite sides of a plane perpendicular to the axes of rotation 17 and 18 .
- the ring gear 12 lies entirely on one side of this plane and the ring gear 14 entirely on the opposite side of the plane.
- the bearing element 35 is preferably designed as a single piece and/or materially integrated. For example, it consists of the same material as the housing shells 22 and 23 . The use of the bearing element 35 enables an especially compact configuration of the final drive 1 , especially in the vertical direction.
- FIG. 3 shows a schematic sectional representation of the final drive 1 , namely, a cross section with respect to the axes of rotation 17 and 19 , the sectioning plane standing perpendicular to the axes of rotation 17 and 18 and preferably containing the axes of rotation 19 and 20 .
- the viewing direction in the cross section is oriented in the direction of the end 29 .
- the input shafts 2 and 4 are not shown here.
- each of the ring gears 13 and 15 or each of the output shafts 7 and 10 is mounted by means of a bearing arrangement 42 in the transmission housing 16 .
- the bearing arrangement 42 for the ring gears 13 and 15 and the corresponding output shafts 7 and 10 are configured analogously, but especially in mirror symmetry. We shall discuss more closely in the following the bearing arrangement 42 for the ring gear 13 and the first output shaft 7 . However, the remarks may always be applied to the bearing arrangement 42 for the ring gear 15 and the second output shaft 10 .
- the bearing arrangement 42 comprises a first radial bearing 43 and a second radial bearing 44 . These are situated in an O-arrangement relative to each other. Alternatively, they may also be designed as a fixed bearing and a floating bearing. In the latter case, one of the radial bearings 43 and 44 forms the fixed bearing and the other of the radial bearings 43 and 44 forms the floating bearing. In the following, however, we shall discuss the O-arrangement shown here. The remarks however may always be applied to the configuration of the radial bearings 43 and 44 as a fixed bearing and a floating bearing.
- the radial bearings 43 and 44 are preferably designed as roller bearings, especially as ball bearings.
- the radial bearings 43 and 44 are both arranged on the first bearing boss 36 . This means that they sit by their inner rings 45 and 46 on the first bearing boss 36 .
- the outer rings 47 and 48 of the radial bearings 43 and 44 are arranged in the ring gear 13 and/or the first output shaft 7 . Accordingly, the outer rings 47 and 48 lie against an inner bearing face 49 of the ring gear 13 or the first output shaft 7 . It is provided that the first radial bearing 43 is braced in the axial direction with respect to the axis of rotation 19 against the center post 40 of the bearing element 35 .
- the first radial bearing 43 is arranged in the axial direction with respect to the axis of rotation 19 between the center post 40 and the ring gear 13 or an axial bearing boss 50 of the ring gear 13 .
- the radial bearing 43 lies permanently against the center post 40 and on the other hand permanently against the axial bearing boss 50 .
- the second radial bearing 44 is preferably secured by a fastening means 51 on the outside in the axial direction, i.e., in the direction facing away from the center post 40 .
- the fastening means 51 used is for example a snap ring or the like.
- the fastening means 51 is releasable.
- the radial bearing 44 is preferably arranged between the fastening means 51 and the ring gear 13 or an axial bearing boss 52 of the ring gear 13 or the first output shaft 7 .
- the second radial bearing 44 lies on the one hand permanently against the fastening means 51 and on the other hand permanently against the axial bearing boss 52 .
- the axial bearing bosses 50 and 52 may be different from each other and in particular they may be arranged with a spacing from each other in the axial direction.
- the axial bearing bosses 50 and 52 may also be designed as a common axial bearing boss, however, wherein the first radial bearing 43 is present on one side and the second radial bearing 44 on the side of this common axial bearing boss facing away in the axial direction. It will be clear that the bearing arrangement 42 , i.e., both the first radial bearing 43 and the second radial bearing 44 , is fastened merely across the bearing element 35 to the transmission housing 16 . The radial bearings 43 and 44 thus engage with the transmission housing 16 solely across the bearing element 35 .
- the first bearing boss 36 comprises a first region 53 as well as a second region 54 , which are different in regard to their diameters.
- the first bearing boss 36 has a first diameter in the first region 53 and a second diameter in the second region 54 , the first diameter being larger than the second diameter.
- the first region 53 preferably borders on the center post 40 , in any case it is situated on the side of the second region 54 facing toward the center post 40 .
- the two regions 53 and 54 preferably adjoin each other directly in the axial direction with respect to the axis of rotation 19 .
- the inner ring 45 has a larger diameter than the inner ring 46 .
- the radial bearings 43 and 44 are the same size in the radial direction, so that analogously to the inner rings 45 and 46 the outer ring 47 has a larger diameter than the outer ring 48 .
- the radial bearings 43 and 44 may be chosen such that the diameter difference between the inner rings 45 and 46 is different from the diameter difference of the outer rings 47 and 48 .
- the inner rings 45 and 46 are designed with different diameters, while the outer rings 47 and 48 have the same diameter.
- FIG. 4 shows a second embodiment of the final drive 1 , once again in a sectional representation.
- reference is made to the preceding remarks and only the differences will be discussed below. These are due to the fact that the radial bearings 43 and 44 of the bearing arrangement 42 are now situated in a tandem arrangement to each other.
- an arrangement of the radial bearings 43 and 44 in an X arrangement or once again—as already explained above—a configuration of the radial bearings 43 and 44 as a fixed bearing and a floating bearing would also be possible.
- the remarks may be applied to the X arrangement and the configuration as a fixed bearing and floating bearing.
- the first radial bearing 43 is arranged analogously to the first embodiment of the final drive 1 . Accordingly, it sits by its inner ring 45 on the first bearing boss 36 . In the axial direction it is braced preferably against the center post 40 on the one hand and against the axial bearing boss 50 on the other hand. However, there are differences with respect to the second radial bearing 44 . This sits by its inner ring 45 on an outer bearing face 55 of the ring gear 13 or the first output shaft 7 . Thus, while the first radial bearing 43 engages with the ring gear 13 or the output shaft 7 , the second radial bearing 44 encloses the ring gear 13 or the output shaft 7 . Consequently, the first bearing boss 36 may be shorter and have a uniform diameter. The fastening means 51 may also be eliminated.
- the second radial bearing 44 engages on the one hand with the ring gear 13 or the output shaft 7 and on the other hand directly with the transmission housing 16 , especially the two housing shells 22 and 23 .
- the axial bearing boss 52 is now formed by a bearing shoulder of the ring gear 13 or the output shaft 7 . This, in turn, can be represented by means of a change in diameter.
- the transmission housing 16 In order to secure the second radial bearing 44 at least on the outside in the axial direction relative to the transmission housing 16 , the transmission housing 16 likewise has an axial bearing boss 56 . This is preferably formed both on the first housing shell 22 and on the second housing shell 23 .
- the second radial bearing 44 now lies between the axial bearing boss 52 and the axial bearing boss 56 , looking in the axial direction with respect to the axis of rotation 19 . Especially preferably, it lies permanently against axial bearing boss 52 on the one hand and permanently against the axial bearing boss 56 on the other hand.
- FIG. 5 shows a first variant of a third embodiment of the final drive 1 .
- the bearing arrangement 42 is designed analogously to the second embodiment described above.
- the axes of rotation 19 and 20 furthermore intersect the axes of rotation 17 and 18 at the points of intersection 33 and 34 , while the points of intersection 33 and 34 may coincide.
- the axes of rotation 19 and 20 respectively intersect both axes of rotation 17 and 18 .
- the axes of rotation 19 and 20 may additionally intersect each other or alternatively be arranged skew to each other, especially spaced apart parallel to each other. In a first variant shown here, the axes of rotation 19 and 20 intersect each other.
- the axes of rotation 19 and 20 are each angled by the same angle relative to the axis plane 21 or the plane of contact 24 , so that the plane standing perpendicular to the plane of contact 24 and containing the axes of rotation 17 and 18 serves as the plane of symmetry for the axes of rotation 19 and 20 .
- FIG. 6 shows a second variant of the third embodiment.
- a sectional representation through the final drive is shown, namely, a longitudinal section view with respect to the axis of rotation 17 and 18 .
- the sectioning plane has been chosen such that the viewing direction is toward the first housing shell 22 .
- the ring gears 12 and 14 of the ring gear transmissions 6 and 9 are arranged on opposite sides of the bearing element 35 .
- the second input shaft 4 passes through the bearing element 35 , in particular it passes through the through opening 41 .
- the direction of driving of the motor vehicle associated with the final drive 1 is indicated by the arrow 57 .
- the axes of rotation 19 and 20 are also set off from each other in the axial direction with respect to the axes of rotation 17 and 18 .
- the ring gear transmissions 6 and 9 are configured such that a cone angle is present, which is different from 90°.
- the cone angle is preferably equal to 90°. The mutual displacement of the axes of rotation 19 and 20 in the axial direction produces two points of intersection 33 and 34 spaced apart from each other.
- the described final drive 1 makes possible an extremely compact configuration. This holds especially when a further transmission mechanism is arranged on the side of the input shafts 2 and 4 facing away from the final drive 1 , especially a differential transmission, preferably an axle differential transmission.
- the final drive 1 serves merely to produce the permanent operative connections between the first input shaft 2 and the first output shaft 7 on the one hand and the second input shaft 4 and the second output shaft 10 on the other hand.
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Abstract
Description
- The invention relates to a final drive for a motor vehicle for a motor vehicle, comprising a first input shaft, a second input shaft, a first output shaft, and a second output shaft, wherein the first input shaft is permanently coupled to the first output shaft by means of a first ring gear transmission and the second input shaft is permanently coupled to the second output shaft by means of a second ring gear.
- The final drive is coordinated with an axle of the motor vehicle, such as a front axle, but preferably a rear axle of the motor vehicle. By means of the final drive, a torque is transmitted from a drive mechanism of the motor vehicle to wheels of the motor vehicle. Put another way, the final drive produces or at least can produce an operative connection between the drive mechanism of the motor vehicle and the axle or its wheels. The drive mechanism is coupled or at least can be coupled permanently to the first input shaft and the second input shaft. For example, the operative connection between the drive mechanism and the two input shafts is present through a transmission mechanism different from the final drive. The transmission mechanism may be designed, for example, as a differential transmission, especially an axle differential transmission. The two input shafts may accordingly be present as Cardan shafts or at least be coupled to Cardan shafts, especially in permanent manner For example, the two input shafts of the final drive are permanently coupled to the output shafts of the transmission mechanism, especially in rigid manner The two output shafts of the final drive are provided at the wheel side, i.e., arranged on a side of the ring gear transmission facing away from the drive mechanism in relation to the flow of torque. The first output shaft for example is associated with a first wheel of the axle and the second output shaft is associated with at least with a second wheel of the same axle, especially coupled to it in a permanent and/or rigid manner Of course, however, it may be provided that the operative connection between the first output shaft and the first wheel and/or the operative connection between the second output shaft and the second wheel can be broken at least temporarily. For this purpose, a shift clutch is provided in the operative connections, especially a claw clutch.
- Within the final drive, the first input shaft is permanently coupled to the first output shaft and the second input shaft is permanently coupled to the second output shaft. The first ring gear transmission and the second ring gear transmission serve for this purpose. By means of the ring gear transmissions, an angled arrangement of the input shafts and the output shafts to each other is achieved. For example, it may be provided that the ring gear transmissions respectively have a hypoid offset, so that the output shafts are arranged with an offset relative to the input shafts, in particular they lie skew to them, i.e., they are arranged at a parallel spacing from them. However, this leads to a large design space requirement for the final drive.
- The problem which the invention proposes to solve is to propose a final drive for a motor vehicle which has advantages over known final drives, especially a reliable mounting of the ring gear transmissions at the same time as having less design space requirement.
- This is accomplished according to the invention by a final drive with the features of claim 1. It is provided that the first input shaft and the second input shaft are arranged coaxial to each other and the first output shaft and the second output shaft extend from the respective ring gear transmission in opposite directions, wherein an axis plane contains the axes of rotation of the input shafts and a plane perpendicular to the axis plane makes an angle of at least 75° and at most 90° with each of the axes of rotation of the output shafts, and that a first ring gear of the first ring gear transmission, which first ring gear is rigidly connected to the first output shaft, and/or a second ring gear of the second ring gear transmission, which second ring gear is rigidly connected to the second output shaft, is mounted in a transmission housing of the final drive in each case by means of a first radial bearing and a second radial bearing, which are arranged in tandem arrangement or in X arrangement to each other or are designed as a fixed bearing and as a floating bearing.
- On the whole, therefore, there is provided a special arrangement of the input shafts and the output shafts as well as a special mounting of at least one of the ring gears, namely, the first ring gears and the second ring gears of the two ring gear transmissions. This arrangement, in turn, makes possible a special configuration of the transmission housing, which is multi-piece, for example. First of all, the two input shafts are arranged coaxial to each other. For example, the second input shaft extends in the first input shaft or vice versa. The two output shafts lie substantially opposite one another, especially in regard to the plane of symmetry, and they extend from the respective ring gear transmission in opposite directions, preferably in the direction of the corresponding wheel of the motor vehicle.
- Both the axis of rotation of the first output shaft and the axis of rotation of the second output shaft for example intersect the two axes of rotation of the input shafts or the common axis of rotation of the input shafts. In other words, it is provided that axes of rotation of the output shafts each intersect the axes of rotation of the input shafts. Accordingly, the ring gear transmissions may be designed without a hypoid offset. However, a design with hypoid offset may also be realized, in which therefore at least the axis of rotation of one of the output shafts does not intersect the axes of rotation of the input shafts. Preferably, however, the axes of rotation of both output shafts do not intersect the axes of rotation of the input shafts in this case. Hence, on the whole, there is a skew arrangement of the axes of rotation of the output shafts relative to the axes of rotation of the input shafts.
- In addition, now, it is provided that the (imaginary) axis plane contains the axes of rotation of the input shafts. The axis plane is arranged substantially horizontal in regard to the installed condition of the final drive. Accordingly, the plane perpendicular to the axis plane, and likewise containing the axes of rotation of the input shafts, is present as a vertical plane, i.e., it is arranged substantially vertically in the installed condition of the final drive. The plane perpendicular to the axis plane at least seem in sectional view, namely, especially in the cross section relative to the axes of rotation of the input shafts, makes an angle of at least 75° and at most 90° with the axes of rotation of the output shafts.
- Each of the axes of rotation thus makes an angle with the plane that fulfills the mentioned preconditions. The angles between the axes of rotation and the plane may be identical, or alternatively they may be different from each other. For example, the angles amount to at least 75° and at most 90°. Preferably, the angle or the angles amount to at least 80°, at least 85°, at least 86°, at least 87°, at least 88° or at least 89°, but always at most 90°. This means that the angle or the angles may be precisely equal to 90° or also less than 90°.
- In addition or alternatively, the plane perpendicular to the axis plane is the plane of symmetry for the axes of rotation of the output shafts at least when seen in sectional view, namely, in particular in the cross section relative to the axes of rotation of the input shafts. The axes of rotation of the output shafts in this case are thus oriented or arranged symmetrically to one another in regard to the plane of symmetry.
- Now, the first ring gear is rigidly connected to the first output shaft and the second ring gear to the second output shaft. The first ring gear is part of the first ring gear transmission, the second ring gear is part of the second ring gear transmission. At least one of these ring gears, but preferably both ring gears, are now mounted in the transmission housing of the final drive, each time by means of two radial bearings, namely, the first radial bearing and the second radial bearing. The two radial bearings are situated in a tandem arrangement or in an X arrangement relative to each other. Alternatively, they may also be designed as a fixed bearing and as a floating bearing. In the latter case, one of the radial bearings forms the fixed bearing and the other of the radial bearings forms the floating bearing. Such an arrangement and/or configuration of the radial bearings enables a reliable and compact mounting of the ring gear or the ring gears on and/or in the transmission housing.
- A further embodiment of the invention provides that the axes of rotation of the two input shafts and the axes of rotation of the two output shafts lie in the axis plane. This represents an especially advantageous orientation of the input shafts and the output shafts, allowing an extremely compact configuration of the final drive. If both the input shafts and the output shafts are arranged in the axis plane, the definition given above using the plane of symmetry is not needed. Accordingly, this is no longer necessary for the definition of the axis plane.
- A further especially preferred embodiment of the invention provides that a bearing element is arranged in the transmission housing, comprising a first bearing boss and a second bearing boss, wherein the ring gear of the first ring gear transmission is mounted on the first bearing boss and the ring gear of the second ring gear transmission is mounted on the second bearing boss. In order to give the final drive an especially compact configuration, the bearing element is arranged in the transmission housing. The bearing element comprises the two bearing bosses, namely, the first bearing boss and the second bearing boss. The bearing bosses serve for the mounting of ring gears of the two ring gear transmissions. Accordingly, the first ring gear of the first ring gear transmission is mounted on the first bearing boss and the second ring gear of the second ring gear transmission is mounted on the second bearing boss. The mounting is preferably directly configured so that the respective ring gear sits on the corresponding bearing boss. However, alternatively a merely indirect mounting may be provided, in which for example the ring gears are mounted on the bearing boss via the respective output shaft. In such a configuration, the output shaft is mounted directly at or on the bearing boss. The mounting of the respective ring gear is provided only indirectly across the output shaft. For example, the ring gear may be spaced apart from the bearing boss in the axial direction with respect to its axis of rotation or the axis of rotation of the output shaft.
- The first ring gear is rigidly joined to the first output shaft or alternatively forms a single piece with it. The same may be provided for the second ring gear and the second output shaft. The bearing element is a mechanism designed separately from the transmission housing. Thus, first of all the transmission housing and the bearing element are fabricated separately from each other and then the bearing element is arranged on or in the transmission housing. Preferably, the bearing element is arranged centrally in the transmission housing, especially centrally with respect to the axes of rotation of the two input shafts. In particular, the axes of rotation of the two input shafts extend through the bearing element, i.e., they intersect it. In order to make possible a simple arrangement of the bearing element in the transmission housing, the latter is preferably multi-piece and comprises for example a first housing shell and a second housing shell. The two bearing bosses for example are round in cross section with respect to their respective longitudinal center axis and preferably emerge in the axial direction from a center post of the bearing element. At their end facing away from the center post, the bearing bosses preferably have a free end.
- A preferred embodiment of the invention provides that the first radial bearing is arranged on the first bearing boss or the second bearing boss for the mounting of the respective ring gear, and/or the second radial bearing is arranged on the transmission housing. Preferably, only one of the two radial bearings, i.e., the first radial bearing and the second radial bearing, is arranged on the first bearing boss, if it is serving for the mounting of the first ring gear, and on the second bearing boss, if it is provided for the mounting of the second ring gear.
- By the arrangement of the radial bearing on the bearing boss is meant that it sits by its inner ring on the respective bearing boss. This means that its inner ring entirely encloses the bearing boss in the circumferential direction and lies against it preferably at least partly continuously, especially entirely continuously, in the circumferential direction. Conversely, this means that the outer ring of the radial bearing engages with the respective ring gear. Hence, a mounting of the ring gear on the transmission housing is provided at least partly via the corresponding bearing boss, so that the ring gear is mounted indirectly on the transmission housing, namely, across the respective bearing boss.
- Preferably, the second radial bearing engages on the one hand with the transmission housing and on the other hand with the ring gear or the corresponding output shaft. For example, for this purpose the second radial bearing sits by its inner ring on the ring gear or the output shaft. The outer ring of the second radial bearing, on the other hand, may be fastened to the transmission housing.
- Accordingly, it is especially preferably provided that one of the radial bearings is arranged on one of the bearing bosses and the other radial bearing engages with the transmission housing. Correspondingly, the ring gear mounted with the aid of the two radial bearings, namely, the first radial bearing and the second radial bearing, is mounted between the bearing boss and the transmission housing, namely, indirectly mounted. Preferably, in this regard, the ring gear is mounted across the first radial bearing directly on the first bearing boss and accordingly indirectly on the transmission housing. On the other hand, the ring gear is mounted across the second radial bearing directly on the transmission housing. This allows for an especially advantageous bracing of the ring gear or the ring gears in the axial direction with respect to their particular axis of rotation.
- A further embodiment of the invention provides that the first radial bearing lies against an inner bearing face of the respective ring gear and the second radial bearing lies against an outer bearing face of the respective ring gear or the output shaft connected to the ring gear. The inner bearing face is formed by a region of the inner circumferential face of the ring gear. The ring gear accordingly has a recess formed coaxial to its axis of rotation or the axis of rotation of the corresponding output shaft. The radial bearing now engages with this recess. For this, preferably the respective bearing boss protrudes into the corresponding ring gear in the axial direction. For example, the bearing boss reaches through an end face of the ring gear, especially an end face of the ring gear facing toward the bearing element.
- While the first radial bearing engages with or lies against the inner bearing face of the ring gear, the second radial bearing engages with the outer bearing face or lies against it. The outer bearing face is formed by an outer circumferential face of the ring gear or the output shaft, which is connected to the ring gear. Preferably, the first radial bearing lies against the ring gear or the output shaft, spaced apart in the axial direction from the second radial bearing. The two radial bearings should accordingly engage with the ring gear or the output shaft at places spaced apart in the axial direction, especially in order to prevent a tilting of the ring gear or the output shaft.
- In a further embodiment of the invention it is provided that the first bearing boss and the second bearing boss emerge from a center post of the bearing element. The center post is accordingly present between the two bearing bosses, which emerge from it on opposite ends of the center post. For example, the center post is arranged roughly centrally in the transmission housing, preferably centrally with respect to the axes of rotation of the input shafts. Preferably the axes of rotation of the input shafts extend at least through the bearing element, but especially through the center post.
- An especially preferred embodiment of the invention provides that the second radial bearing is braced against the transmission housing in the axial direction with respect to the axis of rotation of the respective ring gear. For this, the second radial bearing rests for example by its outer ring against the transmission housing, while it encloses the ring gear or the output shaft with its inner ring. For example, the transmission housing has an axial bearing boss, in order to secure the second radial bearing in the axial direction relative to the transmission housing, on the outside at least in the axial direction, that is, in the direction facing away from the bearing element. Preferably, moreover, the ring gear likewise comprises an axial bearing boss, so that the second radial bearing as a whole, looking in the axial direction, lies on the one hand against the axial bearing boss of the ring gear and on the other hand against the axial bearing boss of the transmission housing and the ring gear as a whole is secured or at least almost secured by the two radial bearings in the axial direction.
- In a further embodiment of the invention it is provided that the bearing element, especially the center post, is fastened to the transmission housing, while the first radial bearing is connected to the transmission housing only via the bearing element. The bearing element is arranged in the transmission housing and secured to it. For example, the bearing element lies against the transmission housing at least for a portion. This holds especially for the center post. Preferably, the bearing element is secured by means of at least one screw to the transmission housing. For example, the transmission housing is multi-piece in design and accordingly it has a first housing shell and a second housing shell. The two housing shells are formed separately from each other and preferably lie against one another in a plane of contact, situated in the axis plane or being parallel to it.
- It may now be provided that the bearing element is fastened to the first housing shell and to the second housing shell, in particular, on opposite sides of the plane of contact or each time by means of at least one screw, whose longitudinal center axis is angled relative to the plane of contact and/or stands perpendicular to it. It may furthermore be provided that the bearing element is respectively fastened to the first housing shell and/or the second housing shell on both sides of an imaginary plane situated perpendicular to the plane of contact and containing a point of intersection of the axes of rotation of the output shafts with the axes of rotation of the input shafts. The radial bearing arranged on the first bearing boss or the second bearing boss is now connected to the transmission housing solely via the bearing element.
- Finally, in a further preferred embodiment of the invention it may be provided that the first radial bearing has a first inner diameter and a first outer diameter and the second radial bearing has a second inner diameter and a second outer diameter, while the first inner diameter is different from the second inner diameter and/or the first outer diameter is different from the second outer diameter. Preferably, however, the difference between the first outer diameter and the first inner diameter is equal to the difference between the second outer diameter and the second inner diameter, so that the two radial bearings have identical dimensions, looking in the radial direction.
- It is preferably provided that the first inner diameter is larger than the second inner diameter and/or the first outer diameter is larger than the second outer diameter. The first radial bearing is accordingly larger in configuration than the second radial bearing, but preferably the difference between the inner diameter and the outer diameter of the two radial bearings is identical in the manner explained above.
- The invention shall now be explained more closely with the aid of the exemplary embodiments represented in the drawing, without this limiting the invention. There are shown:
-
FIG. 1 a schematic side view of a final drive for a motor vehicle, -
FIG. 2 a schematic cross sectional representation through a transmission housing and a bearing element arranged in the transmission housing, -
FIG. 3 a schematic representation of the final drive in a first embodiment, -
FIG. 4 a schematic representation of a second embodiment of the final drive, -
FIG. 5 a first variant of a third embodiment of the final drive in a schematic representation, and -
FIG. 6 a schematic representation of a second variant of the third embodiment of the final drive. -
FIG. 1 shows a schematic side view of a final drive 1 for a motor vehicle. This comprises afirst input shaft 2, of which a connection flange 3 is shown here. Coaxial to thefirst input shaft 2 is arranged a second input shaft 4 not visible here. Thefirst input shaft 2 for this purpose is designed as a hollow shaft and the second input shaft 4 is arranged and/or mounted in thefirst input shaft 2. The second input shaft 4 has aconnection flange 5, which is preferably arranged in the connection flange 3 of thefirst input shaft 2. Thefirst input shaft 2 is permanently coupled by means of a firstring gear transmission 6 to afirst output shaft 7. Thefirst output shaft 7 has aconnection flange 8, which can be seen here. Similarly, the second input shaft 4 is permanently coupled by means of a secondring gear transmission 9 to asecond output shaft 10 permanent, not visible here, having aconnection flange 11. - The first
ring gear transmission 6 consists of aring gear 12 coupled rigidly and permanently to thefirst input shaft 2 and aring gear 13 meshing with thering gear 12 and coupled rigidly and permanently to thefirst output shaft 7. Similarly, the secondring gear transmission 9 comprises aring gear 14 coupled rigidly and permanently to the second input shaft 4 and aring gear 15 meshing with thering gear 14 and coupled rigidly and permanently to thesecond output shaft 10. Thering gear transmissions transmission housing 16 of the final drive 1, especially arranged entirely therein. In other words, thetransmission housing 16 encloses thering gear transmissions - It has already been pointed out that the
first input shaft 2 and the second input shaft 4 are arranged coaxial to each other, whereby the second input shaft 4 lies inside thefirst input shaft 2. Theinput shafts 2 and 4 thus have mutually coinciding axes of rotation 17 and 18. - The
first output shaft 7 and thesecond output shaft 10 now extend from the respectivering gear transmission first output shaft 7 thus extends out from the plane of the drawing, while thesecond output shaft 10 extends into the plane of the drawing. One axis ofrotation 19 of thefirst output shaft 7 or eachconnection flange 8 is arranged slightly slanting in the vertical direction and intersects the axes of rotation 17 and 18. The same holds for an axis ofrotation 20 of thesecond output shaft 10 or itsconnection flange 11, not recognizable here. - The
input shafts 2 and 4 or their axes of rotation 17 and 18 lie in anaxis plane 21, which is situated basically horizontal. Put another way, an imaginary plane stands perpendicular to theaxis plane 21, being the plane of symmetry for the axes ofrotation output shafts rotation axis plane 21 can also be called the vertical plane. - Because the imaginary plane serves as the plane of symmetry for the axes of
rotation rotation rotation 19 thus makes a first angle with respect to theaxis plane 21 or the plane of symmetry and the axis ofrotation 20 makes a second angle with respect to theaxis plane 21 or the plane of symmetry, the two angles being equal. Thus, quite generally, the axes ofrotation axis plane 21. It may also be provided that the axes ofrotation axis plane 21. - In order to make possible a space-saving configuration of the final drive 1, the
transmission housing 16 is multi-piece and comprises afirst housing shell 22 and asecond housing shell 23, which are fabricated separately from each other and rest against one another in a plane of contact 24, lying in theaxis plane 21 or being parallel to it. Thefirst housing shell 22 and thesecond housing shell 23 are joined together by means of at least onescrew 25, in the exemplary embodiment shown here by means of a plurality ofscrews 25. At least one of thescrews 25, but preferably all of thescrews 25, now has alongitudinal center axis 26 which is angled relative to the plane of contact 24, i.e., which intersects it at a particular angle. Accordingly, it is not provided that thescrew 25 or itslongitudinal center axis 26 is arranged parallel to the plane of contact 24 or that thelongitudinal center axis 26 lies in the plane of contact 24. Instead, especially preferably, thelongitudinal center axis 26 stands perpendicular to the plane of contact 24. Furthermore, it is preferably provided that at least one of thescrews 25 is penetrated by the plane of contact 24, i.e., it is intersected by the plane of contact 24. - This means, for the arrangement of the
screw 25, that the screw is present at the side on thetransmission housing 16 and not, for example, on a separate fastening flange provided on a top side or a bottom side of thetransmission housing 16 for the fastening of theshells - With such a configuration the design space requirement in the vertical direction, i.e., in the plane of symmetry, can be significantly reduced as compared to other final drives 1.
- Against the
first housing shell 22 lies afirst bearing face 27, situated in the plane of contact 24, and against thesecond housing shell 23 lies asecond bearing face 28, situated in the plane of contact 24. The two bearing faces 27 and 28 lie flush against each other, especially over the entire surface, after the assembling of thehousing shells face 27 lies against the entiresecond bearing face 28. Each of the bearing faces 27 and 28 accordingly fully covers the respective other bearing face 28 or 27. - The
screw 25 now passes through both thefirst bearing face 27 and thesecond bearing face 28. Accordingly, it engages with thefirst housing shell 22 and with thesecond housing shell 23 to fasten them to each other. In the exemplary embodiment represented here, it is provided that thefirst bearing face 27 extends in the direction of the axes of rotation 17 and 18 from oneend 29 of thetransmission housing 16 to itsother end 30. In addition or alternatively, this holds for thesecond bearing face 28. Especially preferably, therefore, both thefirst bearing face 27 and thesecond bearing face 28 extend on the one hand as far as theend 29 and on the other hand as far as theend 30. - Between the
ends first output shaft 7 or itsconnection flange 8 as well as a second exit opening 32 for thesecond output shaft 10 or itsconnection flange 11. Thefirst output shaft 7 accordingly passes through the first exit opening 31 or is situated therein, while thesecond output shaft 10 passes through the second exit opening 32 or is situated therein. - Especially preferably, it is provided that the
exit openings housing shell 22 and thesecond housing shell 23. However, at least each of theexit openings first housing shell 22 and at least partly in thesecond housing shell 23. The bearing faces 27 and 28 thus each comprise two partial faces, which are situated on opposite sides of theexit openings -
FIG. 2 shows a schematic partial sectional representation of a portion of the final drive 1. Theinput shafts 2 and 4 as well as theoutput shafts ring gear transmissions rotation 19 intersects the axes of rotation 17 and 18 at a point ofintersection 33. This also holds analogously for the axis ofrotation 20 at a point ofintersection 34 not shown here, which may coincide with the point ofintersection 33. - Furthermore, it is now recognizable that a bearing
element 35 is arranged in thetransmission housing 16 in a preferred embodiment of the final drive 1. This comprises afirst bearing boss 36 and, situated opposite to this, asecond bearing boss 37, not recognizable here. Rotationally mounted on thefirst bearing boss 36 is thefirst ring gear 13, rigidly connected to thefirst output shaft 7, and on thesecond bearing boss 37 is mounted thering gear 15 of the secondring gear transmission 9, rigidly connected to thesecond output shaft 10. Thefirst bearing boss 36 protrudes in the direction of thefirst exit opening 31, in particular it protrudes into it or even passes through it in the direction of the axis ofrotation 19. Conversely, thesecond bearing boss 37 protrudes in the direction of thesecond exit opening 32. It also may protrude into it or even pass through it in the direction of the axis ofrotation 20. - The bearing
element 35 is now fastened on the one hand to thefirst housing shell 22 and on the other hand to thesecond housing shell 23. The fastening occurs each time by means of at least onescrew 38, preferably each time by means ofseveral screws 38. This is recognizable here only for the fastening of the bearingelement 35 to thesecond housing shell 23. Preferably, however, the corresponding remarks may be applied to the fastening of the bearingelement 35 to thefirst housing shell 22. It can be seen that thescrew 38 or thescrews 38 each have alongitudinal center axis 39. Thescrew 38 or itslongitudinal center axis 39 is now angled with respect to the plane of contact 24 (not shown here). In particular, it stands perpendicular to the plane of contact 24. This means therefore that thelongitudinal center axis 39 of thescrew 38 is oriented preferably parallel to thelongitudinal center axis 26 of thescrew 25. - The
screw 38 engages in acenter post 40 of the bearingelement 35 in order to hold thebearing element 35 on thetransmission housing 16. The bearingbosses center post 40 on opposite sides of the plane of symmetry. Furthermore, a throughopening 41 may be formed in thecenter post 40, especially between the bearingbosses element 35, especially its throughopening 41, in the axial direction with respect to the axes of rotation 17 and 18. - The
ring gear transmissions input shafts 2 and 4 are present on opposite sides of the bearingelement 35, i.e., on opposite sides of a plane perpendicular to the axes of rotation 17 and 18. In particular, thering gear 12 lies entirely on one side of this plane and thering gear 14 entirely on the opposite side of the plane. The bearingelement 35 is preferably designed as a single piece and/or materially integrated. For example, it consists of the same material as thehousing shells element 35 enables an especially compact configuration of the final drive 1, especially in the vertical direction. -
FIG. 3 shows a schematic sectional representation of the final drive 1, namely, a cross section with respect to the axes ofrotation 17 and 19, the sectioning plane standing perpendicular to the axes of rotation 17 and 18 and preferably containing the axes ofrotation end 29. Theinput shafts 2 and 4 are not shown here. It can be seen that each of the ring gears 13 and 15 or each of theoutput shafts bearing arrangement 42 in thetransmission housing 16. The bearingarrangement 42 for the ring gears 13 and 15 and thecorresponding output shafts bearing arrangement 42 for thering gear 13 and thefirst output shaft 7. However, the remarks may always be applied to thebearing arrangement 42 for thering gear 15 and thesecond output shaft 10. - The bearing
arrangement 42 comprises a firstradial bearing 43 and a secondradial bearing 44. These are situated in an O-arrangement relative to each other. Alternatively, they may also be designed as a fixed bearing and a floating bearing. In the latter case, one of theradial bearings radial bearings radial bearings radial bearings - The
radial bearings first bearing boss 36. This means that they sit by theirinner rings first bearing boss 36. The outer rings 47 and 48 of theradial bearings ring gear 13 and/or thefirst output shaft 7. Accordingly, the outer rings 47 and 48 lie against an inner bearing face 49 of thering gear 13 or thefirst output shaft 7. It is provided that the firstradial bearing 43 is braced in the axial direction with respect to the axis ofrotation 19 against thecenter post 40 of the bearingelement 35. In other words, the firstradial bearing 43 is arranged in the axial direction with respect to the axis ofrotation 19 between thecenter post 40 and thering gear 13 or anaxial bearing boss 50 of thering gear 13. In particular, theradial bearing 43 lies permanently against thecenter post 40 and on the other hand permanently against theaxial bearing boss 50. - The second
radial bearing 44 is preferably secured by a fastening means 51 on the outside in the axial direction, i.e., in the direction facing away from thecenter post 40. The fastening means 51 used is for example a snap ring or the like. In particular, the fastening means 51 is releasable. Theradial bearing 44 is preferably arranged between the fastening means 51 and thering gear 13 or anaxial bearing boss 52 of thering gear 13 or thefirst output shaft 7. Preferably, the secondradial bearing 44 lies on the one hand permanently against the fastening means 51 and on the other hand permanently against theaxial bearing boss 52. - The
axial bearing bosses axial bearing bosses radial bearing 43 is present on one side and the secondradial bearing 44 on the side of this common axial bearing boss facing away in the axial direction. It will be clear that the bearingarrangement 42, i.e., both the firstradial bearing 43 and the secondradial bearing 44, is fastened merely across the bearingelement 35 to thetransmission housing 16. Theradial bearings transmission housing 16 solely across the bearingelement 35. - Furthermore, it can be seen that the
first bearing boss 36 comprises afirst region 53 as well as asecond region 54, which are different in regard to their diameters. Thus, thefirst bearing boss 36 has a first diameter in thefirst region 53 and a second diameter in thesecond region 54, the first diameter being larger than the second diameter. Thefirst region 53 preferably borders on thecenter post 40, in any case it is situated on the side of thesecond region 54 facing toward thecenter post 40. The tworegions rotation 19. - The first
radial bearing 43 now sits in thefirst region 53 and the secondradial bearing 44 in thesecond region 54 on thefirst bearing boss 36. Accordingly, theinner ring 45 has a larger diameter than theinner ring 46. Preferably, theradial bearings inner rings outer ring 47 has a larger diameter than theouter ring 48. Of course, however, theradial bearings inner rings outer rings inner rings outer rings -
FIG. 4 shows a second embodiment of the final drive 1, once again in a sectional representation. Basically, reference is made to the preceding remarks and only the differences will be discussed below. These are due to the fact that theradial bearings arrangement 42 are now situated in a tandem arrangement to each other. Alternatively, an arrangement of theradial bearings radial bearings - The first
radial bearing 43 is arranged analogously to the first embodiment of the final drive 1. Accordingly, it sits by itsinner ring 45 on thefirst bearing boss 36. In the axial direction it is braced preferably against thecenter post 40 on the one hand and against theaxial bearing boss 50 on the other hand. However, there are differences with respect to the secondradial bearing 44. This sits by itsinner ring 45 on an outer bearing face 55 of thering gear 13 or thefirst output shaft 7. Thus, while the firstradial bearing 43 engages with thering gear 13 or theoutput shaft 7, the secondradial bearing 44 encloses thering gear 13 or theoutput shaft 7. Consequently, thefirst bearing boss 36 may be shorter and have a uniform diameter. The fastening means 51 may also be eliminated. - The second
radial bearing 44 engages on the one hand with thering gear 13 or theoutput shaft 7 and on the other hand directly with thetransmission housing 16, especially the twohousing shells axial bearing boss 52 is now formed by a bearing shoulder of thering gear 13 or theoutput shaft 7. This, in turn, can be represented by means of a change in diameter. In order to secure the secondradial bearing 44 at least on the outside in the axial direction relative to thetransmission housing 16, thetransmission housing 16 likewise has anaxial bearing boss 56. This is preferably formed both on thefirst housing shell 22 and on thesecond housing shell 23. The secondradial bearing 44 now lies between theaxial bearing boss 52 and theaxial bearing boss 56, looking in the axial direction with respect to the axis ofrotation 19. Especially preferably, it lies permanently againstaxial bearing boss 52 on the one hand and permanently against theaxial bearing boss 56 on the other hand. -
FIG. 5 shows a first variant of a third embodiment of the final drive 1. Once again, a schematic cross sectional representation is shown according to the preceding remarks. The bearingarrangement 42 is designed analogously to the second embodiment described above. However, it is also possible to use abearing arrangement 42 according to the first embodiment. In this respect, reference it made to the preceding remarks. In the following, only the differences from the first embodiment shall be discussed. These consist in the fact that the ring gears 13 and 15 and hence the axes ofrotation - This means that the axes of
rotation intersection intersection rotation rotation rotation rotation axis plane 21 or the plane of contact 24, so that the plane standing perpendicular to the plane of contact 24 and containing the axes of rotation 17 and 18 serves as the plane of symmetry for the axes ofrotation -
FIG. 6 shows a second variant of the third embodiment. A sectional representation through the final drive is shown, namely, a longitudinal section view with respect to the axis of rotation 17 and 18. The sectioning plane has been chosen such that the viewing direction is toward thefirst housing shell 22. Reference is made expressly to the preceding remarks. In addition to these, it is now clearly recognizable here that the ring gears 12 and 14 of thering gear transmissions element 35. For this—as already explained above—the second input shaft 4 passes through the bearingelement 35, in particular it passes through the throughopening 41. The direction of driving of the motor vehicle associated with the final drive 1 is indicated by thearrow 57. - In addition or alternatively to the first variant described above, in which the axes of
rotation rotation ring gear transmissions rotation intersection - The described final drive 1 makes possible an extremely compact configuration. This holds especially when a further transmission mechanism is arranged on the side of the
input shafts 2 and 4 facing away from the final drive 1, especially a differential transmission, preferably an axle differential transmission. Thus, the final drive 1 serves merely to produce the permanent operative connections between thefirst input shaft 2 and thefirst output shaft 7 on the one hand and the second input shaft 4 and thesecond output shaft 10 on the other hand.
Claims (21)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016218731.7 | 2016-09-28 | ||
DE102016218731.7A DE102016218731B4 (en) | 2016-09-28 | 2016-09-28 | Axle drive for a motor vehicle |
PCT/EP2017/074227 WO2018060136A1 (en) | 2016-09-28 | 2017-09-25 | Final drive for a motor vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
US20200032888A1 true US20200032888A1 (en) | 2020-01-30 |
Family
ID=59955574
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/337,592 Abandoned US20200032888A1 (en) | 2016-09-28 | 2017-09-25 | Final drive for a motor vehicle |
Country Status (5)
Country | Link |
---|---|
US (1) | US20200032888A1 (en) |
EP (1) | EP3519228B1 (en) |
CN (1) | CN109789773A (en) |
DE (1) | DE102016218731B4 (en) |
WO (1) | WO2018060136A1 (en) |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1771487A (en) * | 1930-03-17 | 1930-07-29 | Int Motor Co | Driving mechanism |
DE1059299B (en) | 1956-05-26 | 1959-06-11 | Kloeckner Humboldt Deutz Ag | Drive for motor vehicles with two semi-axles |
DE2937594A1 (en) | 1978-11-14 | 1980-05-29 | Gkn Axles | Differential gear assembly for vehicle - has differential unit located to one side of crown-wheel and pinion sets |
JPH0725270B2 (en) * | 1986-02-05 | 1995-03-22 | 富士重工業株式会社 | Rear wheel torque distribution control device for vehicle |
DE3710582A1 (en) | 1986-03-31 | 1987-11-12 | Shinwa Sangyo Co | Permanent four wheel drive for a motor vehicle |
JPH02296040A (en) | 1989-05-11 | 1990-12-06 | Shinwa Sangyo Kk | Limited differential device |
DE102007003675A1 (en) * | 2007-01-25 | 2008-07-31 | Schaeffler Kg | Spur gear differential for motor vehicle, has planetary gearing, planet carrier formed as sum wheel and two difference shafts that are coaxially arranged for sum wheel, which forms output for spur gear differential |
DE102009005343A1 (en) * | 2009-01-16 | 2010-07-22 | Sew-Eurodrive Gmbh & Co. Kg | Bevel gear transmission has block-shaped housing with drive side and output side, where ring-shaped reinforcement is equipped in drive side around through-opening |
DE102009012463B3 (en) * | 2009-03-12 | 2010-11-25 | Gkn Driveline International Gmbh | Angle drive arrangement |
DE202009014189U1 (en) * | 2009-10-20 | 2011-03-03 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Electric machine for an electrical axle of a motor vehicle |
FR2953773B1 (en) * | 2009-12-16 | 2012-04-27 | Michelin Soc Tech | MOTORIZED HUB COMPRISING MEANS FOR COUPLING AND DECOUPLING. |
CN103842200B (en) * | 2011-10-01 | 2016-06-29 | 麦格纳动力系有限两合公司 | Transfer gear |
-
2016
- 2016-09-28 DE DE102016218731.7A patent/DE102016218731B4/en not_active Expired - Fee Related
-
2017
- 2017-09-25 EP EP17772061.2A patent/EP3519228B1/en active Active
- 2017-09-25 WO PCT/EP2017/074227 patent/WO2018060136A1/en unknown
- 2017-09-25 CN CN201780059629.5A patent/CN109789773A/en active Pending
- 2017-09-25 US US16/337,592 patent/US20200032888A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
DE102016218731A1 (en) | 2018-03-29 |
EP3519228A1 (en) | 2019-08-07 |
CN109789773A (en) | 2019-05-21 |
WO2018060136A1 (en) | 2018-04-05 |
EP3519228B1 (en) | 2021-06-02 |
DE102016218731B4 (en) | 2021-09-30 |
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